DE102010018086A1 - Heat transferring device e.g. boiler, for transferring heat between heat transfer median streams, has heat exchanger whose inclined longitudinal axis is arranged in angular range greater and less than specified range in relation to warm end - Google Patents

Abstract

The device (20) has a plate heat exchanger (21) with four connecting pieces (25, 28, 29, 32) for supplying and discharging heat transfer fluids. The exchanger is arranged at an angle, and channels of the exchanger are vertically extended in relation to direction of gravity (G). A warm end (22) and a cool end (33) of the exchanger are upwardly and downwardly arranged in relation to the direction of gravity. An inclined longitudinal axis (L) of the exchanger is arranged in an angular range that is greater than 90 degree and less than 180 degree in relation to the warm end.

Description

The present invention relates to heat transfer devices according to the preambles of claims 1, 5 and 8. Such heat transfer devices use heat exchangers and are used for both media cooling and heating.

It is known, heat exchangers, also plate heat exchanger 1 Especially in district heating stations with their longitudinal axis L parallel to the direction of gravity G to arrange what in the 1 is shown, or at right angles. In the arrangement of the longitudinal axis L of the plate heat exchanger 1 at right angles to the direction of gravity G, the plates 2 itself parallel (vertical) or at right angles to the direction of gravity G (horizontal), which is in the 2 and 3 is shown. In the parallel arrangement of the longitudinal axis L of the heat exchanger 1 to the direction of gravity G, it is customary, the warm of the connecting piece HWW (hot water input hot), DHW (DHW output warm) of the heat transfer media both below (see. 1 ) as well as above (not shown) and accordingly the cold of the connecting pieces HWK (heating water outlet cold), TWK (drinking water input cold) above (see. 1 ) or below (not shown). In the arrangement of the longitudinal axis L of the plate heat exchanger 1 at right angles to the direction of gravity G and the plates 2 parallel to the direction of gravity G, it is customary, the colder 3 of the heat transfer media in the upper half of the longitudinal axis L of the heat exchanger 1 to let flow (cf. 2 ).

Furthermore, it is known, the longitudinal axis L of the plate heat exchanger 1 of water heaters 10 Although upright, but not parallel to the direction of gravity G to arrange, but in the direction of their width by an angle between 10 ° and 45 ° obliquely, with a heat exchanger connection 11 to the hot water tap from the lower two heat exchanger connections 11 . 12 the higher located with respect to the direction of gravity G is (see the German Utility Model DE 20 2008 003 349 U1 ), what in 4 is shown.

In this case, mixing effects occur in particular in the case of small or stalled flow and / or in the case of particularly large differences in temperature and density in the heat exchanger channels, since the direction of flow of the heat transfer media is directed against the natural density-related stratification. Although these mixing effects reduce the calcification on the drinking water side, as the hot heat transfer medium is reduced in its temperature. On the other hand, inevitably increases the return temperature. However, low return temperatures are a condition for optimal use of all heat sources.

In the parallel (cf. 1 ), vertical (cf. 2 ) or inclined (cf. 4 ) Arrangement of the longitudinal axis L of the plate heat exchanger to the direction of gravity G occurs when a vertical pipe guide up or down or sideways to a collision between the connecting pipes superimposed nozzle and the incorporated devices such as pumps, filters, fittings, sensors, etc. This is justified in that adjacent nozzles TWK, HWK, or TWW, HWW of heat exchangers 1 often have a small distance, since they are designed to be closer to an ideal countercurrent rather narrow and a long thermal length than a large "thermal width".

In the arrangement of the longitudinal axis L of the plate heat exchanger 1 and the plates 2 even at right angles to the direction of gravity G (cf. 3 Although this problem is better solvable, as in 5 is shown. The heat exchanger 1 but represents the lowest point and the largest cross section of the system and it is easy in the flow channels for the accumulation of solid components from the heat transfer media, which can not be flushed out at low flow rates. As a result, deposits, a deterioration of the heat transfer and higher return temperatures with the known negative consequences. Furthermore, it comes with larger temperature and density differences to layering phenomena and so to an uneven loading of the individual horizontal channels, especially at partial load. The consequence of this is also higher return temperatures, local overheating / undercooling, thermal stresses, deposits, etc. Particularly difficult is a change in the heat exchanger required in the further consequence 1 , which usually has a high mass and must be moved vertically during assembly / disassembly and held. The vertical pipe guide upwards and the free space for the assembly / disassembly of the heat exchanger 1 down a relatively high construction can arise (see. 5 ).

The present invention is based in a first aspect, the problem to be solved that in a conventional arrangement of the heat exchanger in heat transfer devices, the flow channels are applied unevenly, in the flow channels mixing phenomena or negatively impacting stratification appear, the systems not particularly compact and / or are easy to install and maintenance.

According to this aspect, the object is achieved with a heat transfer device according to claim 1. Advantageous developments are the subject of the dependent subclaims.

In a second aspect of the invention, a heat transfer device is to be provided, which is particularly insensitive to calcification when the device is at a standstill, and in particular also very energy-efficient.

According to this aspect, the object is achieved with a heat transfer device according to claim 5. Advantageous developments are the subject of the dependent subclaims.

In a third aspect of the invention, a heat transfer device is to be provided which ensures minimum return temperatures during operation and, in particular in water heaters, further reduces the risk of calcification.

According to this aspect, the object is achieved with a heat transfer device according to claim 8.

The heat transfer device according to the invention for the transfer of heat between at least two heat transfer media streams has in a first aspect of the invention, a heat exchanger with at least four connecting pieces for the supply and discharge of heat transfer media, preferably a plate heat exchanger, wherein the heat exchanger is arranged inclined, and characterized in that with respect to the direction of gravity, the channels of the heat exchanger extend vertically, the warm end of the heat exchanger above and the cold end of the heat exchanger are arranged below, with respect to the warm end, the inclined longitudinal axis of the heat exchanger in an angular range greater than 90 ° and smaller 180 ° is arranged.

In this context are meant as ends those sides of the heat exchanger through which the longitudinal axis extends. The warm end is the end at which the connecting piece for the input of the warmer of the two heat transfer media is arranged, and the cold end is the end to which the connecting piece for the input of the colder of the two heat transfer media is arranged.

The advantages that can be achieved are, in particular, that both the uniform distribution of the media streams to the various flow channels and a minimum mixing in the flow channels takes place through the thermodynamically and mechanically optimal arrangement of the heat exchanger, as well as very compact systems arise, the easy to install, low maintenance and easy to maintain are.

In an expedient development, the connecting pieces of the colder heat transfer media in the upper half and the connecting pieces of the warmer of the heat transfer media are arranged in the lower half with respect to the inclined longitudinal axis of the heat exchanger. As a result, a particularly effective heat transfer takes place even at very low flow rates, since the colder medium sinks down and the warmer rises to the top and thus optimal stratification and smallest temperature differences can be ensured in this arrangement.

In an advantageous embodiment, it is provided that the angle of the inclination of the longitudinal axis of the heat exchanger is at least so large that the lower edge of the free cross section of the upper of the two connecting pieces of the heat transfer media streams is at least as high as the upper edge of the free cross section of the lower connection piece the same heat transfer medium flow. This makes it possible that even at low flow rates and intensive stratification in the flow channels a minimum return temperature or maximum flow temperature can be achieved with minimal heat transfer media throughput and systems can be designed particularly flat with inclined heat exchangers arranged.

The fact that extend from the upper and lower connecting pieces connecting pipes which extend parallel to each other and vertically upwards or downwards, wherein the angle of inclination of the longitudinal axis of the heat exchanger is so large that the connecting pipes in a for the assembly, maintenance and / or thermal insulation sufficient horizontal distance from each other, it is surprisingly possible to build the heat transfer device is particularly narrow, with no kinking pipes as in the DE 20 2008 003 349 U1 ( 4 ) must be used. The guideline for the sufficient distance is that the pipes can not touch each other and that standard tools can be used without injuring themselves during assembly. If an insulation is to take place, these insulation elements must be attachable without hindrance. Ultimately, this is considered to be sufficient distance from the exact dimensions of the connecting pieces and pipes and the possibly used insulating elements.

Independent protection is claimed for the heat transfer device according to the invention for the transfer of heat between at least two heat carrier media streams, which in a second aspect of the invention a Heat exchanger having at least four connecting pieces for the supply and discharge of heat transfer media, in particular plate heat exchanger, and is characterized in that after the upper and / or lower connection piece, a thermal siphon is led away vertically upwards or downwards.

As a result, in particular the water heater is protected against calcification at a standstill. In addition, this embodiment can also be combined as desired with the features of the heat transfer device according to the first aspect of the invention.

In an advantageous development, it is provided that the siphon is designed coaxially and / or thermally insulated and / or equipped with sensors or sensors. The coaxial design reduces the construction cost and the external heat transfer surface of the siphon. This and a thermal insulation reduce heat loss or heat absorption to / from the environment. The arrangement of the sensor or sensor in the siphon, especially in the interior of a coaxial siphon immediately behind the upstream connection piece of the heat exchanger prolongs the effect of the desired temperature enclosed in the siphon dormant heat transfer medium to the control loop. Thus, the supply of the acting heat transfer medium is delayed accordingly, reduced energy consumption, reduces the calcification in particular of water heaters. Depending on the task, the heat transfer media, the sensor length, the flow rates, etc., an optimal siphon size can be found, ie. H. to determine its diameter and length / height. A larger siphon content worsens the control accuracy during operation, but possibly extends the standstill phases without additional heat input.

In an expedient development of the heat transfer device according to both the first and the second aspect of the invention, it is provided that the colder heat transfer medium is fresh water. This is especially preferred for hot water.

Independent protection is claimed for the heat transfer device according to the invention for the transfer of heat between at least two heat transfer media streams, which in a third aspect of the invention comprises a heat exchanger with at least four connecting pieces for the supply and discharge of heat transfer media, in particular plate heat exchanger, and characterized in that a circulation pump is arranged after the hot water outlet.

This ensures that during operation, the return temperature is further minimized and, especially in water heaters, the calcification risk is reduced. In addition, this embodiment can also be combined as desired with the features of the heat transfer devices according to the first and / or second aspect of the invention.

In addition to the representations of the known prior art, embodiments of the present invention are illustrated in the drawings and will be described in more detail below to explain the features and advantages of the present invention in more detail. Show it:

1 - A plate heat exchanger, especially in district heating stations with the longitudinal axis parallel to the axis of gravity;

2 A plate heat exchanger with the longitudinal axis at right angles and the plates themselves parallel to the axis of gravity;

3 A plate heat exchanger with the longitudinal axis and the plates at right angles to the axis of gravity;

4 - A domestic water heater with a sloping transformer, the transformer connection to the hot water tap from the lower two transformer terminals the higher in the direction of gravity, according to DE 20 2008 003 349 U1 ;

5 - A water heater with the arrangement of the longitudinal axis of the plate heat exchanger and the plates at right angles to the axis of gravity and the connecting pipes vertically upwards;

6a - a two-stage water heater;

6b - a single-stage water heater;

6c - a single-stage heating radiator;

6d - a two-stage heating radiator, and

7 - Another arrangement of a heat exchanger according to the invention.

In the figures described below, the same elements are given the same reference numerals, and not all the elements shown are designated in each figure.

In 6a is the heat transfer device according to the invention 20 for a two-stage water heater with the heat exchanger 21 shown purely schematically. It can be seen that the longitudinal axis L of the plate heat exchanger 21 in terms of the warm end 22 of the heat exchanger 21 is arranged inclined by 115 ° to the direction of gravity G. A heat exchanger is used 21 for at least three heat transfer media according to DE 100 07 574 A1 , with reference to this document with regard to the design of the heat exchanger 21 and its functioning is fully referenced.

In the top of the inclined longitudinal axis L area 23 of the heat exchanger 21 enters cold fresh water 24 with 10 ° C and flows at one in the outlet nozzle 28 of the hot water supply 30 arranged sensor of a thermostatic valve (not shown) - as will become apparent - warms over. To comply with the set hot water temperature of 60 ° C, the thermostatic valve opens, leaving a certain stream of district heating primary flow water 27 over the sloping under the hot water pipe 28 located inlet 29 with 110 ° C enter. Due to the high temperature and the resulting lower density compared to the cooled district heating return water 26 in the same channels the hot district heating supply water rises 27 in the flow channels along the upper short side 22 of the plate heat exchanger 21 on. There it flows almost parallel with the other channels in the target temperature of 60 ° C warming and thus also emerging cold fresh water 24 , This cools the district heating supply water 27 in cocurrent to min. 61-62 ° C from. At the top, it flows around the outlet nozzle 28 of hot water 30 and is deflected to the upper long side of the plate heat exchanger 21 in countercurrent with the heating from 55 ° C to 60 ° C circulation return 31 on min. 56-57 ° C to be cooled.

On the way from the common inlet 32 of cold fresh water 24 and the circulation return 31 to your own return pipe 25 stream the district heating water 27 and the cold fresh water 24 also in cocurrent along the lower short side at the cold end 33 of the plate heat exchanger 21 , The district heating return 27 occurs with min. 15-20 ° C from the channels of the plate heat exchanger 21 in the outlet 25 , This up to max. 25 ° C preheated fresh water 24 is redirected at this. It continues to flow along the lower long side of the plate heat exchanger 21 in countercurrent to 45 ° C also separated in the primary flow pipe 29 introduced heating return water 34 and heats up slowly to max. 43-44 ° C. The heating return water 34 Thus, in a second stage, depending on the volume flow ratio further up to min. Chilled 26-27 ° C and occurs together with the coming from above 15-20 ° C cold return water 27 out. In the outlet 25 there is a mixing of the two return streams 27 . 34 to 26 with about 21-24 ° C.

Comes with missing hot water tap 24 and deactivated hot water circulation 31 the flow in the plate heat exchanger 21 to stop, so long as possible to grant that no hot district heating 27 in the plate heat exchanger 21 is initiated and there may be a calcification on the hot water side of the warm end 22 leads. The sensor of the hot water temperature of the thermostatic valve is for this purpose in a vertical portion of a thermal siphon (not shown) immediately behind the outlet nozzle 28 arranged. The thermal siphon is designed as a coaxial double tube and is particularly effectively insulated against heat losses. The emerging hot water 30 gets from the hot primary 27 heated and rises via free convection in the isolated siphon. The thermostat sensor located in the coaxial double tube closes the control valve safely until the hot water 30 again cooled below 60 ° C. Because of the good thermal insulation of the siphon this takes about 20-30 minutes, so that only max. 2-3 times an hour a small amount of primary supply water 27 is re-fed to temper the siphon content. This primary supply water 27 has cooled down in the meantime and the risk of calcification is therefore reduced. The standing water in the heat exchanger 21 also cools below the calcification temperature. This is specifically promoted by the design of the piping / fittings (not shown) and / or the heat exchanger 21 without thermal insulation, and possibly in addition by the further through the heat exchanger 21 flowing heating return water 34 , The siphon has comparatively large flow cross sections and in it prevail at tapping and circulation high flow velocities, so that it can not come to a Kalkststopfung here. In a hot water tap 24 or a resumption of circulation 31 Immediately warm water 30 available from the siphon. The return 26 however, is - without the flow of heating return water 34 cooled down to room temperature.

Thus, there is a pronounced density coating in the flow channels with small hot water taps and flow arrest and there is a high control quality. Only with stronger hot water tap 30 the channels are flowed through more uniformly and the DC zones along the short sides 22 . 33 of the plate heat exchanger 21 increasingly turn to cross and / or Countercurrent zones between the warming fresh water 24 and the particularly intensively cooling district heating primary water 27 , This is the result of the inclined arrangement of the heat exchanger 21 in every operating condition of the water heater 20 to minimum return temperatures. Low return temperatures are known to result in a particularly high efficiency of the district heat generator, low heat losses, a small Fernwärmeumwälzmenge and a low pump energy consumption.

The arrangement of the circulation pump in the hot water supply 30 in the flow direction behind the heat exchanger 21 (not shown) conditional on an arrangement in the circulation return 31 in front of the heat exchanger 21 that at every hot water tap 30 the circulation volume flow 31 is reduced by just tapped hot water volume. This also leads to a lower district heating return temperature. The arranged by the suction circulation pump in the heat exchanger 21 lowered water pressure also acts a shift in the solution equilibrium by heating the fresh water 24 and thus leads to less precipitation and deposition of lime. The arrangement of the circulation pump under the siphon causes the residual heat of the circulation pump rises after their decommissioning in the isolated part of the siphon.

The 115 ° inclined arrangement of the heat exchanger 21 leads to an offset in the horizontal arrangement of the connection piece 32 . 25 respectively. 28 . 29 , This leads to a similar offset of the vertically upwards or alternatively downwardly led away connecting lines (only hinted at). Since these additionally in two levels behind the heat exchanger 21 are guided, is the water heater 20 Even with the largest thermal power of about 300 kW with 400 mm × 670 mm × 1,200 mm (T × W × H) particularly simple and compact. So it is possible, in the same dimensions, a standardized series of water heaters 20 to realize a wide variety of services. The sizes differ only in the number of plates of the heat exchanger 21 and the diameter of the connecting pipes, fittings and technological equipment. Their arrangement is, however, by the type of heat exchanger selected 21 and its inclination angle predetermined and always the same.

Once it is necessary, the plate heat exchanger 21 This can be done very easily from the beginning. These are the throws or flanges on the connecting piece 25 . 28 . 29 . 32 of the heat exchanger 21 from the sides 22 . 33 accessible.

It should not go unmentioned that the inclined arrangement of a heat exchanger 21 can be used equally advantageous for all similar applications, such. B. for single-stage water heaters 40 (see. 6b ) as well as 50 or multi-level heating radiator 60 (see. 6c and 6d ), etc., wherein the single-stage Heizwärmekereiter 50 the connecting piece 32 at the cold end 33 of the heat exchanger 21 the heating return 51 and the connecting piece 28 the warm end 22 the heating flow 52 leads.

Multi-level heating radiator 60 (see. 6d ) and multi-stage water heaters 20 (see. 6a ) can be coupled in an ideal manner in a district heating connection station according to DE 10 2008 038 617 A1 , with reference to this document with respect to the design of the heat exchanger, their coupling and their functioning is fully referenced. In this regard, the district heating return is circulation 35 in 6a noted. Through this, primary medium with a temperature of about 57 ° C, which results when no hot water extraction takes place, out and into the port 35 of the two-stage heating radiator 60 in 6d fed.

The minimum angle of inclination of a plate heat exchanger 21 in a further preferred embodiment of the heat transfer device according to the invention 70 arises when the bottom edge 71 . 72 the two laterally arranged nozzle 29 . 28 the warm end 22 of the heat exchanger 21 is arranged at least as high in free cross section, as the top edge 73 . 74 the lower side-mounted nozzle 25 . 32 of the same heat transfer medium flow in free cross section, as in 7 is indicated. In this case, in this example, the longitudinal axis L is opposite to the direction of gravity G with respect to the warm end 22 arranged inclined by 94 °. Then comes out of the return pipe 25 always only cooled heat transfer medium.

The maximum angle of inclination of the plate heat exchanger 21 results when the vertically upwardly or alternatively downwardly guided parallel connection pipes are still in a sufficient for the assembly and maintenance and thermal insulation horizontal distance to each other (not shown). A smaller angle of inclination thus leads to a wider but flatter design of the hot water module, a greater inclination angle - to a narrower but higher version.

Thus, radiators, ie heat transfer devices with the purpose of the cooling are advantageously to be arranged in inclined form (not shown). Here is also the heat transfer medium to be cooled in the lower part of the Longitudinal axis of an inclined Plattenwärmeübertragers led down. As a result, very little cooling water is needed because it always exits at the highest possible temperature. The pin assignments are the same in terms of the temperature of the media, the flow directions as well. But while in a heating device, the colder heat transfer medium is considered, which is to be heated, the warmer heat transfer medium is considered in a cooling device, which is to be cooled, of course, both processes always run simultaneously.

Also, of course, all other forms and types of heat exchangers can advantageously be arranged inclined according to the invention, such. B. tube bundle, spiral heat exchanger, combined apparatus with heat exchangers, such as. B. boiler or heat storage itself or only their heat exchanger inside, etc.

Likewise, the heat transfer media can assume other states of aggregation than the liquid or also change these in the heat exchanger.

In the present case were heat exchangers 21 described in which the two heat transfer media streams 3 . 4 are guided parallel to each other, that in relation to the inclined longitudinal axis L, the connecting piece 25 . 28 . 29 . 32 every stream 3 . 4 are either above or below. Alternatively, however, it can also be provided that the currents 3 . 4 crossed over to each other, in which case the connecting piece of each stream 3 . 4 with respect to the longitudinal axis L are opposite to each other. This increases the thermal length and replaces the DC zones with more effective cross-flow zones from the outset.

It is also conceivable, with knowledge of the teaching according to the invention, to develop and advantageously arrange trapezoidal heat exchangers whose warm or cold ends are inclined vertically or evenly or non-uniformly with respect to the longitudinal axis and whose upper and / or lower sides are parallel or at an angle to one another and are arranged evenly or non-uniformly inclined to the gravity axis, so that possibly only the or individual nozzles have a height offset (not shown). Thus, the available space could be better utilized and a more uniform flow through the channels and different thermal lengths for possibly multi-stage heat exchanger can be achieved.

Of course, it is also possible to arrange round or similar heat exchangers, in particular round or oval plate heat exchangers according to the invention so that their connecting pieces have an advantageous height offset (not shown).

Circulation pumps and / or siphons, especially for the inclusion of sensors, of course, not only in the hot water line of a water heater, but also in all other similar embodiments, arrangements and applications according to the invention advantageously arranged in the flow direction behind a heat exchanger.

For all these applications, equal protection is sought, always with the aim of evenly distributing the media streams to and minimizing mixing in the various flow channels, as well as creating very compact systems that are easy to install, low maintenance and easy to service.

LIST OF REFERENCE NUMBERS

1

Plate heat exchangers

2

Plates of the plate heat exchanger

G

The direction of gravity

L

Longitudinal axis of the heat exchanger

CDW

Connecting piece drinking water inlet cold

TWW

Connecting piece Drinking water outlet warm

HWW

Connecting piece heating water inlet warm

HWK

Connecting piece heating water outlet cold

3

first heat transfer medium flow

4

second heat transfer medium flow

10

Water heater

11

Connecting piece of drinking water warm

12

Connecting piece heating water warm

20

Heat transfer device

21

Heat exchanger

22

warm end of the heat exchanger

23

Upper area of the heat exchanger

24

Drinking water cold

25

Connecting piece of district heating return

26

District heating return

27

District heating primary flow water

28

Connecting piece of drinking water warm

29

Connecting piece of the district heating advance

30

hot water

31

Circulation return water

32

Connecting piece of drinking water cold

33

cold end of the heat exchanger

34

Heating return water

35

District heating return circulation

40

single-stage water heater

50

single-stage heating radiator

51

Heating return water

52

Heating flow water

60

Multi-stage heating radiator

70

Heat transfer device

71

Bottom edge of connection plug for district heating

72

Bottom edge of connecting pipe drinking water warm

73

Top edge connection pipe drinking water cold

74

Top edge of connecting pipe district heating return

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 202008003349 U1 [0003, 0018, 0029]
• DE 10007574 A1 [0037]
• DE 102008038617 A1 [0046]

Claims (8)

Heat transfer device ( 20 ; 40 ; 50 ; 60 ; 70 ) for the transfer of heat between at least two heat transfer media streams with a heat exchanger ( 21 ) with at least four connecting pieces ( 25 . 28 . 29 . 32 ) for the supply and discharge of the heat transfer media, preferably a plate heat exchanger, wherein the heat exchanger ( 21 ) is inclined, characterized in that with respect to the direction of gravity (G) - the channels of the heat exchanger ( 21 ) extend vertically, - the warm end ( 22 ) of the heat exchanger ( 21 ) above and - the cold end ( 33 ) of the heat exchanger ( 21 ) are arranged below, with respect to the warm end ( 22 ) the inclined longitudinal axis (L) of the heat exchanger ( 21 ) is arranged in an angular range greater than 90 ° and less than 180 °. Heat transfer device ( 20 ; 40 ; 50 ; 60 ; 70 ) according to claim 1, characterized in that with respect to the inclined longitudinal axis (L) of the heat exchanger ( 21 ) the connecting pieces ( 28 . 32 ) of the colder heat transfer media in the upper half ( 23 ) and the connecting pieces ( 25 . 29 ) of the warmer of the heat transfer media are arranged in the lower half. Heat transfer device ( 70 ) according to claim 1 or 2, characterized in that the angle of inclination of the longitudinal axis (L) of the heat exchanger ( 21 ) is at least so large that the lower edge ( 71 . 72 ) of the free cross section of the upper ( 28 . 29 ) of the two connecting pieces ( 25 . 28 . 29 . 32 ) of the heat transfer media streams is at least as high as the top edge ( 73 . 74 ) of the free cross section of the lower connecting piece ( 25 . 32 ) of the same heat carrier media stream. Heat transfer device according to one of the preceding claims, characterized in that extending from the upper and lower connecting pieces connecting pipes which extend parallel to each other and vertically upwards or downwards, wherein the angle of inclination of the longitudinal axis of the heat exchanger is so large that the connecting pipes in a sufficient for the installation, maintenance and / or thermal insulation horizontal distance to each other. Heat transfer device for the transfer of heat between at least two heat transfer media streams with a heat exchanger with at least four connecting pieces for the supply and discharge of heat transfer media, preferably a plate heat exchanger, in particular according to one of the preceding claims, characterized in that after the upper and / or lower connection piece thermal siphon is led away vertically up or down. Heat transfer device according to claim 5, characterized in that the siphon is coaxial and / or thermally insulated and / or equipped with sensors or sensors. Heat transfer device ( 20 ; 40 ; 50 ; 60 ; 70 ) according to one of the preceding claims, preferably for hot water preparation, characterized in that the colder heat transfer medium is fresh water. Heat transfer device for the transfer of heat between at least two heat transfer media streams with a heat exchanger with at least four connecting pieces for the supply and discharge of heat transfer media, preferably a plate heat exchanger, in particular according to claim 7, characterized in that a circulation pump is arranged after the hot water outlet.

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